Hydraulic crushing machine

ABSTRACT

The crushing machine particularly adapted for crushing autmobile bodies is a portable trailer unit. The trailer body includes a bed defined by a horizontal base platform, end frame structures, and stringers connecting the upper ends of the end frame structures. A rear deck extending from the bed carries the trailer supporting wheels, and a forward deck carries the tractor coupling. A horizontal crusher ram is supported in overlying relation to the bed by parallel hydraulic subsystems pivotally connected between the body end frames and the crusher ram, these systems providing multiple bearing points for transmitting force to the crusher ram. One side panel for the bed is vertically shiftable to permit loading and unloading.

United States Patent 1 Allbritton Oct. 29, 1974 HYDRAULIC CRUSHINGMACHINE Primar Examiner-Bill J. Wilhite 6 l t: w11 R.Allbtt ,27 lMll y Y[7 1 men or gg 23 0d 1 Attorney, Agent, or FirmPeter J. Murphy; Cecil L.

Wood [22] Filed: Aug. 24, 1973 [21] Appl. No.: 391,309

[57] ABSTRACT 52 US. Cl 100 100 74 520, 100 DlG.l, 1 {00/272 {00/286 Thecrushing machme particularly adapted for crush- 51 Int. Cl 6301) 1/16aumwbile bodies is a Portable trailer The [58] new of Search 100/100 271272 DIG 1 trailer body includes a bed defined by a horizontal 100/286.254/124. 4 4 6 base platform, end frame structures, and stringers con- 674/106 6 necting the upper ends of the end frame structures. A rear deckextending from the bed carries the trailer [56] References Citedsupporting wheels, and a forward deck carries the tractor coupling. Ahorizontal crusher ram is sup- UNITED STATES PATENTS ported in overlyingrelation to the bed by parallel hy- Warnken X connected Rig s; body endframes and the crusher ram, these systems 3 625 078 12/1971 Bourassaa";l'iiijjil'jllil''stt/124 x pmvdmg multple bearmg f for transm'ttilg 3642 250 2 1972 Klopp 254 124 force the crusher one we Panel for the bed337571680 9/1973 Williams 100/10 vertically shiftable to permit loadingand unloading. 3,799,728 3/1974 Howard 425/DIG. 222

9 Claims, 5 Drawing Figures HYDRAULIC CRUSIIING MACHINE BACKGROUND ANDSUMMARY OF THE INVENTION This invention relates to portable metalcrushing apparatus and more particularly to hydraulic crushing apparatusfor crushing automobile bodies and the like.

It is the principal object of this invention to provide a crushingapparatus for automobile bodies which is adapted to be towed from placeto place by means of a suitable tractor, which has sufficient crushingforce for the efficient crushing of automobile bodies and the like, andwhich is of a weight and size to be conveniently moved from one locationto another on public highways, to minimize the necessity for specialtravel permits and to enable passage through standard underpasses.

It is another object of this invention to provide such portable crushingapparatus which is ready for operation with little or no set up time ata new location and which, by the same token, requires little or no knockdown time prior to movement to a new location.

A further object of this invention is to provide such apparatus havingan improved hydraulic system to minimize the weight and mass of thecrusher ram.

For accomplishing these objects a crushing machine consists of a bodyincluding a crusher bed defined by a generally horizontal platform forsupporting an article to be crushed, end frames extending upwardly fromopposite ends of the bed, horizontal stringers connecting the upper endsof the end frames, and upright walls at the periphery of the bed forrestricting lateral flow of the crushed metal. A generally horizontalcrusher ram disposed above the crusher bed for vertical movement towardand away from the bed is supported and powered by a hydraulic powersystem including two hydraulic subsystems operating in generallyparallel vertical planes, powered by a motor driven hydraulic pump andsystem supported on the body. Each planar subsystem includes first andsecond hydraulic power cylinders each having one end pivotally attachedto the crusher ram intermediate the ends thereof and extendingrespectively toward opposite ends of the ram. First and second scissorsassemblies are associated respectively with the first and second powercylinders, each scissors assembly having an upper and lower armpivotally connected at one end to each other and to the other end of itsassociated power cylinder. The free end of each upper scissors arm ispivotally connected to a respective end frame adjacent to the upper endthereof; and the free end of each lower scissors arm is pivotallyconnected to the crusher ram adjacent to the respective end thereof. Thepivotal connections of the two lower scissors arms and the two powercylinders to the crusher ram define at least three and preferably fourspaced bearing points of the hydraulic sybsystem transmitting force tothe crusher ram, with the two hydraulic subsystems defining at least sixand preferably eight spaced bearing points.

The novel features and the advantages of the invention, as well asadditional objects thereof, will be understood more fully from thefollowing description when read in connection with the accompanyingdrawings.

DRAWINGS FIG. I is a perspective view of a crushing machine ac cordingto the invention;

FIG. 2 is a side view of the machine of FIG. I, showing the crusher ramin the upper position;

FIG. 3 is a top view of the apparatus of FIG. 1;

FIG. 4 is another side view of the apparatus of FIG. 1 illustrating thecrusher ram in the lower position; and

FIG. 5 is a fragmentary sectional view taken in the plane 5-5 of FIG. 2.

DESCRIPTION OF THE PREFERRED EMBODIMENT In the drawings, the crushingmachine according to the invention is embodied in the form of a traileradapted to be transported over the highways by means of a suitabletractor vehicle. The overall trailer is illustrated in FIGS. 1 through4, with the crusher ram being shown in the raised position in FIGS. 1and 2, in condition for loading an automobile body onto the machine bed,and in the lower most position in FIG. 4 which would be the position ofthe crusher ram when the trailer is being moved from one location toanother.

Referring to these Figures, the crushing machine body 10 includes anelongated crusher bed 11 defined by a generally horizontal platformwhich extends for a substantial portion of the length of the trailer andmay have a ground clearance for example of about 1 foot when in thetransport mode as seen in FIG. 2. A front frame structure 12 and a rearframe structure 13 extend upwardly from the bed 11 to a height of 2.5feet, for example, from the base of the bed, or an overall ground heightof 13.5 feet. The frame structures are joined at the top by longitudinalframe or stringer members l4 and 15 thereby defining a box-like bodystructure.

A rear deck structure 16 extends rearwardly from the rear framestructure 13 and is rigidly supported relative to the rear frame byangle braces 17. The rear deck 16 carries the tandem trailer wheelassembly 18 for supporting the rear end of the trailer, so that the bedis maintained at approximately the I foot ground clearance abovementioned.

A front deck structure 20 extends forwardly from the front frame 12,generally horizontally, and is rigidly supported relative to the frontframe by angle braces 21. This front deck 20 carries the coupler 22 onits under side for engagement with the mating coupler of a towingtractor.

A tractor 25, illustrated fragmentarily in FIGS. 2, 3 and 4 includes achassis 26, drive wheels 27, cab 28 and coupler assembly 29.

The above described body is fabricated from suitable structural steelmembers such as I beams, H beams and plates. The stringers l5 and 14 forexample may be fabricated of I beams or H beams; and, while only twosuch stringers are shown, the number and strength of these stringers areselected to withstand the required compression and tensile forces forsupporting the trailer body 10 and for absorbing the reaction forcesduring operation of the crusher ram as will be described.

A preferred form of structure for the bed II is particularly illustratedin FIG. 5, the bed consisting of sideby-side I-I beams 31 and elongatedplates 32 welded in an integral assembly wherein the plates supplementthe H beam webs and providing additional beam strength. Transverseplates or straps 33 may be welded to the under side of this H beamstructure to provide additional transverse beam strength for the bed.

As an example of the bed structure, the bed may be fabricated of seven14 X 12 inch H beams for example welded in side-by-side relation withthe intervening supplementary beam plates being fabricated of 13 V2 Xinch steel plates. These members being welded into an integratedassembly as above described. The additional transverse straps or platesmay also be fabricated of inch steel plate. A length of the bed assemblymay be in excess of 20 feet.

The front and rear frame structures define end walls for the bed l andside walls are defined by side panels 35 and 36, the panel 35 on theright side of the trailer being a fixed panel, and the panel 36 on theleft side of the trailer being a sliding panel or gate. The two panelsare generally similar in structure being constructed of a frame work ofstructural channels 37 for example with the interior walls beingfabricated of metal plates 38 welded to the frames.

The sliding panel 36 is guided for vertical sliding movement withinvertical guide slots 39 provided in the front and rear frames at theleft side of the trailer, as best seen in FIG. 1. As best seen in FIG.2, the sliding panel is provided with suitable ears extending from theends thereof which are guided in the slots 39; and double actinghydraulic power cylinder or jacks 40 are positoned within the front andrear frame structures and coact with brackets 41 secured to the slidingpanel for railing and lowering the panel. The raised position of thesliding panel 26 is illustrated in phantom lines in FIG. 4; and in thisposition an auto body may be placed on the machine bed by means of afork lift for example.' The crushed auto body is removed from the bed ina similar manner.

The panel 36 is shown fragmentarily in cross-section in FIG. and in thisview it is seen that the lower edge of the panel may be provided withdownward projecting pins 42 for engagement in mating holes in theconfronting surface of the bed, for the purpose of inhibiting lateralmovement of the panel 26 during the crush- I ing of an auto body.Several such pins 42 may be provided intermediate the ends of the panel,where the bending moment is greatest.

The crusher ram 45 is a planar member which may have a structure similarto that of the bed 1; that is being fqbricated of side-by-side H beamswelded together, either with or without intervening plates to supplementthe H beam webs for longitudinal beam strength. The beam strengthrequired for the pressure ram may not be so great because of themultiple bearing points provided by the hydraulic system to bedescribed; and accordingly the structural members which make up thecrusher ram need not be as heavy as those for the bed. For lateral beamstrength, the crusher ram also may include plates or horizontal strapswhich are welded to the top of the crusher ram structure. The crusherram is dimensioned to be closely received within the confining walls ofthe bed defined by the end frames and the side panels and 36.

A hydraulic system for supporting the crusher ram and for applying thecrushing force thereto is best illustrated in FIGS. 1 and 2, with thecrusher ram shown in the raised position. The hydraulic system consistsof two subsystems 46 and 46a functioning respectively at the left andright sides of the crusher ram and body, these systems being describedas planar since they function generally in parallel vertical planesadjacent to the opposite sides of the crusher ram. Since the subsystemsare identical, the subsystem at the left side of the ram will bedescribed, with the counterpart components of the other subsystem beingindicated by the same reference numbers with the subscript a.

The subsystem 46 consists of two double acting hydraulic power cylinders50 and 51 which are disposed in overlapping or staggered relation, withthe cylinder 50 being disposed toward the front end of the crusher ramand the cylinder 51 being disposed toward the rear. The cylinder of thepower cylinder 50 is pivotally attached to the crusher ram by means of abracket 52 to swing in a vertical plane relative to the crusher ram; andthe power cylinder 51 is similarly pivotally mounted to the crusher bymeans of a bracket 53 again to swing in a vertical plane. Due to thestaggered relation, while the power cylinder 50 is the front cylinder,its pivot bracket 52 is nearer the rear end of the crusher ram while thebracket 53 for the rear cylinder 51 is nearer the front end of the ram.

The extension rod 54 for the front power cylinder 50 is pivotallyattached to a scissors assembly consisting of an upper arm 55 and alower arm 56, the inner ends of these arms also being pivoted relativeto each other at the pivot connection to the extension rod. As best seenin FIG. 2 the front end of the upper arm 55 is pivotally connected tothe front frame 12 by means of a bracket 57; and the lower arm 56 ispivotally connected to the front end of the crusher ram by means of abracket 58. it will be seen then that the assembly of power cylinder 50and its associated scissors arms 55 and 56 is anchored at one point tothe front frame at the bracket 57, and at two points to the crusher ramat the brackets 52 and 58.

Similarly the extension rod 64 of the power cylinder 61 is pivotallyattached to a scissors assembly consisting of an upper arm 65 and lowerarm 66, with the upper am being pivotally connected to the rear frame 13adjacent to its upper end by means of the bracket 67, and with the lowerarm being pivotally connected to the crusher ram adjacent to its rearend by means of a bracket 68. Again the assembly of the power cylinder51 and its associated scissors arms is connected to the crusher ram attwo points, and to the body rear frame at one point.

Looking at the overall hydraulic subassembly 46 then, which functionsgenerally in a vertical plane adjacent to the left hand edge of thecrusher ram 45, this subassembly is connected to the body at two pointsnamely the bracket 57 and 67, and is connected to the crusher ram atfour points namely the brackets 58, 53, 52 and 68. The brackets 52 and53, and the bearing points defined thereby, are located generally in thecenter of the length of the ram and, depending upon the function forwhich the crushing machine is designed, could be pivotally connected ata common center point, or the bearing points could be spacedsubstantially as shown to define separated central bearing points.

The hydraulic subassembly 46a is identical in structure, and fucntionsin an identical manner acting along the right hand edge of the crusherram 45. The overall hydraulic assembly then consisting of subassemblies45 and 46 is pivotally attached to the body 10 at four points overlyingthe four corners of the rectangular crusher ram 45; and is connected tothe crusher ram at eight points which are relatively uniformlydistributed over the area of the pressure ram to provide for good forcedistribution to the ram and to make possible a ram structure of lighterweight and strength than would be required if the force were applied tothe ram at bearing points fewer in number and less uniformlydistributed.

Other components of the hydraulic system are conveniently mounted on therear deck 16 and rear frame 13 for example. The hydraulic system isconventional, and illustrated components include a reservoir 71conveniently mounted on the rear deck 16, an electric motorpump assembly72 mounted on a reservoir 71, and a manually operable control valveassembly 73 mounted on the rear frame 13 for convenient manual controland operation of the several power cylinders. While an electric motor isillustrated for the motor-pump assembly 72, it will be appreciated thatother sources of power such as internal combustion engines may beemployed.

A feature of the hydraulic power system for the crusher ram is thearrangement of the power cylinders and associated scissors assemblieswherein the components thereof are disposed generally horizontally whenthe ram 45 is in its uppermost position as best seen in FIG. 2, with thescissors arms extending from the common pivot connection with the powercylinder extension rod and forming an acute angle at this pivot pointwhich may be as little as 30 for example. Each arm of the respectivescissors assembly then would be disposed approximately one half thatamount or relative to a horizontal plane, and the associated powercylinder would have an angle of inclination of less that 15 relative tothe horizontal so that the line of force when the power cylinderextension rod is extended is directed along a line between the axis ofthe two arms or within the acute angle formed by the two arms.

As the crusher ram begins to move downward, relatively little force isrequired, and indeed the weight of the ram will assist in this movementuntil such time at least as the ram contacts the uppermost portion ofthe automobile body to be crushed. With the beginning of the crushingaction, the force required will increase and will continue to increaseas the auto body continues to be compacted or crushed.

The particular arrangement of the crusher ram hydraulic system lendsitself well to this situation since, due to the leverage action providedby the scissors assemblies, the downward components of force exerted atthe several bearing points increases as the distance of the ram from theupper starting position increases.

Comparing FIG. 4 with FIG. 2, it will be seen that the angle of thepower cylinders increase to a relatively small degree during movementfrom the uppermost ram position to the lowermost ram position and thisof course will effect an increase of the downward component of forceacting on the power cylinder bearing points defined by the brackets 52,52a, 53 and 53a. The multiplication of the downward component of forcesby the scissors assembly is much more pronounced however, these forcesacting on the bearing points defmed by the ram bracket 58, 58a, 68 and68a. Referring to the FIG. 2 position, the horizontal components offorce acting on the brackets 67 and 68 for example are much greater thanthe vertical components of force acting on these brackets. As theassembly approaches the FIG. 4 position however, the horizontalcomponents of force acting on the brackets approach zero while thevertical components of force acting on these brackets are multipliedmany times from the original vertical components. In otherwords, withthis system, the vertical component of force, which is the crushingforce is greatest toward the end of the compacting stroke where thegreatest force is required.

A trailer crushing machine as above described may be designed to haveample crushing force for the intended purpose, and yet have a weight andsize limitation which permits movement over state and federal highwayswith minimum inconvenience. For example, the trailer may be designed tohave a length which, when combined with the length of the towingtractor, will not exceed 55 feet and a gross weight of the trailer andtractor assembly which will not exceed 72,000 lbs. Additionally themaximum height of the trailer will not exceed 13 feet 6 inches and themaximum width will not exceed 8 feet. Under present regulations, unitswhich exceed these criteria may not be moved in certain areas and atcertain times without special permit; and additionally a vehicle havinga greater height may not be able to negotiate certain underpasses,possibly requiring travel of many additional miles to enable transportfrom one particular location to another.

Since all of the functions during operation of the crushing machine areaccomplished hydraulically, the machine is well adapted to be operatedeither manually at the unit, or could be operated manually at a locationremote from the unit through suitable remote control connections, and itcould also be operated automatically through a programmed controlmechanism.

OPERATION The trailer crushing machine as shown in the transport mode inFIG. 4 where it is coupled to a towing tractor 25, wherein the crusherram 45 is positioned at its lowermost position, and wherein the slidingpanel 36 is positioned at its lowermost position. For the transportmode, suitable blocks may be positioned between the crusher bed 11 andthe crusher ram so that the weight of the ram is supported by the blocksrather than by the hydraulic support system.

When the machine arrives at a working location, there is little or noset up required to prepare the machine for use. Since the crushingforces'are absorbed entirely within the body 10 it would not benecessary to support the body by auxiliary means, although this wouldprobably be desirable.

Since the machine is a hydraulically controlled and operated machine, itwould be convenient to provide hydraulic jacks for supporting the body10 during operation. This then would permit removal of the tractor unitand remove the load from the rear wheel assembly 18. Alternatively, thejacks could be employed to temporarily raise the body 10 so a sufficientheight to insert leveling timbers between the ground surface and theunder surface of the bed, and then lower the body for support on thesetimbers during crushing operations. Another possible construction isthat the rear wheel assembly 18 may be removable from the rear deck 16to permit lowering of the crusher bed nearer to ground level.

Considering these alternatives, the set up time to place the crushingmachine in condition for operation is very small. By the same token,when the operation is completed at that location and the machine is tobe moved to another location. the knock down time, or the time requiredto ready the machine for the transport mode, is correspondingly small.

For the crushing operations, both the crusher ram and the sliding panelare raised to their upper positions to permit loading of an automobilebody from the side by means of a fork lift for example. FIG. 2illustrates the machine in loaded condition ready for the crushingoperation, with the sliding panel 36 lowered to restrain lateralexpansion of the auto body during crushing. The controls are thenactuated to extend the power cylinders 50 and Sll to vertically compressthe auto body to the required extent. If desired, a second auto bodycould be placed over the first body already crushed, with a secondcrushing operation then being effected so that the sandwiched bodies oftwo autos may then be removed in a single operation.

What has been described is a crushing machine particularly adapted forthe crushing of bodies of automobiles or other vehicles, which isdesigned to be transportable over state and federal highways withminimum inconvenience, and which requires little or no set up time forthe purpose of commencing crushing operations and correspondingly littleor no knock down time for the purpose of preparing the device for thetransport mode following crushing operations.

While the preferred embodiment of the invention has been illustrated anddescribed, it will be understood by those skilled in the art thatchanges and modifications may be resorted to without deparing from thespirit and scope of the invention.

What is claimed is:

l. A crushing machine comprising a body including a crusher bed definedby a generally horizontal platform for supporting an article to becrushed, end frame means extending upwardly from the opposite ends ofsaid bed, horizontal stringer means connecting the upper ends of saidend frame means, and upright wall means at the periphery of said bed forrestricting lateral flow of the crushed metal; generally horizontalcrusher ram disposed above said crusher bed for vertical parallelmovement toward and away from said bed;

a hydraulic power system for supporting and powering said crusher ramincluding two hydraulic subsystems operating in generally parallelvertical planes, and a motor driven hydraulic pump for supplyingpressurized hydraulic fluid to said subsysterns;

each planar hydraulic subsystem including first and second hydraulicpower cylinders each having one end pivotally attached to said crusherram intermediate the ends thereof and extending respectively towardopposite ends of said ram; first and second scissors assembliesassociated respectively with said first and second power cylinders, eachscissors assembly having an upper and lower arm pivotally connected, atone end, to each other and to the other end of its associated powercylinder; the free end of each upper scissors arm being pivotallyconnected to a respective end frame adjacent to the upper end thereof,and the free end of each lower scissors arm being pivotally connected tothe crusher ram adjacent to a respective end; the pivotal connections ofsaid two lower scissors arms and said two power cylinders to saidcrusher ram defining at least three spaced bearing points of thehydraulic subsystem transmitting force to said crusher ram;

and said two hydraulic subsystems defining at least six spaced bearingpoints for the transmission of force to said planar crusher ram.

2. A crushing machine as set forth in claim 1 wherein said one ends ofthe first and second hydraulic power cylinders of a hydraulic subsystemare pivotally attached to said crusher ram at spaced points intermediatethe ends thereof, whereby each hydraulic subsystem defines four bearingpoints for the transmission of force to said crusher ram, and wherebysaid two subsystems define eight spaced bearing points for transmittingforce to said crusher ram.

3. A crushing machine as set forth in claim 2 wherein the first andsecond power cylinders of a subsystem overlap each other with the oneend of said first cylinder being pivotally attached to said .crusher ramnearer the end of the ram remote from the pivotal connection of itsassociated scissors assembly; and with the second hydraulic powercylinder having its one end pivotally attached to the crusher ram nearerthe end of the ram remote from the pivotal connection of its associatedscissors assembly.

4. A crushing machine as set forth in claim 1 wherein the cylinder endsof the several hydraulic power cylinders are the one ends which arepivotally attached to said crusher ram intermediate the ends thereof;and wherein the extension rod ends of the several power cylinders arethe ends which are pivotally connected to the respective scissorsassembly.

5. A crushing machine as set forth in claim 1 wherein the four hydraulicpower cylinders of the two hydraulic subsystems are connected to a common hydraulic pump for the uniform application of force to the severalbearing points of said crusher ram.

6. A crushing machine as set forth in claim 1 wherein one of saidupright wall means is movable vertically for permitting loading andunloading of the machine bed from one side.

7. A crushing machine as set forth in claim 6 including hydraulic powercylinder means disposed at each end of the vertically movable wall forraising and lowering said wall relative to the machine bed.

8. A crushing machine as set forth in claim 1 said body defining aportable trailer adapted to be towed by a tractor; said body including adeck extending from the rearward end of the bed for carrying the rearsupporting wheels of the trailer body; and said body including a deckextending from the forward end of said bed for carrying a coupler forcoupling to a towing tractor.

9. A crushing machine as set'forth in claim 8 wherein said hydraulicpump and its power driving means are supported on one of said decks.

1. A crushing machine comprising a body including a crusher bed definedby a generally horizontal platform for supporting an article to becrushed, end frame means extending upwardly from the opposite ends ofsaid bed, horizontal stringer means connecting the upper ends of saidend frame means, and upright wall means at the periphery of said bed forrestricting lateral flow of the crushed metal; a generally horizontalcrusher ram disposed above said crusher bed for vertical parallelmovement toward and away from said bed; a hydraulic power system forsupporting and powering said crusher ram including two hydraulicsubsystems operating in generally parallel vertical planes, and a motordriven hydraulic pump for supplying pressurized hydraulic fluid to saidsubsystems; each planar hydraulic subsystem including first and secondhydraulic power cylinders each having one end pivotally attached to saidcrusher ram intermediate the ends thereof and extending respectivelytoward opposite ends of said ram; first and second scissors assembliesassociated respectively with said first and second power cylinders, eachscissors assembly having an upper and lower arm pivotally connected, atone end, to each other and to the other end of its associated powercylinder; the free end of each upper scissors arm being pivotallyconnected to a respective end frame adjacent to the upper end thereof,and the free end of each lower scissors arm being pivotally connected tothe crusher ram adjacent to a respective end; the pivotal connections ofsaid two lower scissors arms and said two power cylinders to saidcrusher ram defining at least three spaced bearing points of thehydraulic subsystem transmitting force to said crusher ram; and said twohydraulic subsystems defining at least six spaced bearing points for thetransmission of force to said planar crusher ram.
 2. A crushing machineas set forth in claim 1 wherein said one ends of the first and secondhydraulic power cylinders of a hydraulic subsystem are pivotallyattached to said crusher ram at spaced points intermediate the endsthereof, whereby each hydraulic subsystem defines four bearing pointsfor the transmission of force to said crusher ram, and whereby said twosubsystems define eight spaced bearing points for transmitting force tosaid crusher ram.
 3. A crushing machine as set forth in claim 2 whereinthe first and second power cylinders of a subsystem overlap each otherwith the one end of said first cylinder being pivotally attached to saidcrusher ram nearer the end of the ram remote from the pivotal connectionof its associated scissors assembly; and with the second hydraulic powercylinder having its one end pivotally attached to the crusher ram nearerthe end of the ram remote from the pivotal connection of its associatedscissors assembly.
 4. A crushing machine as set forth in claim 1 whereinthe cylinder ends of the several hydraulic power cylinders are the oneends which are pivotally attached to said crusher ram intermediate theends thereof; and wherein the extension rod ends of the several powercylinders are the ends which are pivotally connected to the respectivescissors assembly.
 5. A crushing machine as set forth in claim 1 whereinthe four hydraulic power cylinders of the two hydraulic subsystems areconnected to a common hydraulic pump for the uniform application offorce to the several bearing points of said crusher ram.
 6. A crushingmachine as set forth in claim 1 wherein one of said upright wall meansis movable vertically for permitting loading and unloading of themachine bed from one side.
 7. A crushing machine as set forth in claim 6including hydraulic power cylinder means disposed at each end of thevertically movable wall for raising and lowering said wall relative tothe machine bed.
 8. A crushing machine as set forth in claim 1 said bodydefining a portable trailer adapted to be towed by a tractor; said bodyincluding a deck extending from the rearward end of the bed for carryingthe rear supporting wheels of the trailer body; and said body includinga deck extending from the forward end of said bed for carrying a couplerfor coupling to a towing tractor.
 9. A crushing machine as set forth inclaim 8 wherein said hydraulic pump and its power driving means aresupported on one of said decks.